Co-generation and control method of the same

ABSTRACT

Disclosed related to a co-generation comprising a heat exchanger heating water; a heat transfer path connected with the water heat exchanger to transfer heat; a hot water storage tank connected with the water heat exchanger and the water circulation path; a hot water storage water supply apparatus supplying water in the hot water storage tank to the water circulation path; a water supply path connected with the water circulation path; a water supply apparatus supplying water to the water supply path; and a hot water supply heat exchanger bypassing apparatus and bypassing the water supplied to the water circulation path from the hot water storage tank through the hot water supply heat exchanger. The co-generation of the present invention has some advantage in that the effective water boil heat is increased as supplying the cold water supplied from the water service and the hot water supplied from the hot water storage tank to the hot water supply heat exchanger  70  properly and heat exchanging with the heat medium such as an anti freezing solution and etc passing through the hot water supply heat exchanger.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a co-generation and the control methodof the same in which waste heat of an engine is transferred to ahot-water supply heat exchanger by an antifreeze solution and so on and,more particularly, to a co-generation and the control method of the samemaximizing the efficiency of hot water supply by controlling the watersupply and the heat storage in accordance with the temperature of watersupplied from outside, of hot water storage tank storing the waterheated in the hot-water supply heat exchanger, and the temperature ofthe heat medium streaming into the hot-water supply heat exchanger.

2. Description of the Conventional Art

FIG. 1 is a block diagram of the co-generation according to theconventional art.

The conventional co-generation, as depicted in FIG. 1, comprises anelectric generator 2 generating electricity, a drive source 10(hereinafter referred to as “engine”) such as an engine and etcgenerating heat as well as driving the electric generator 2, a wasteheat recovery apparatus 20 recovering the waste heat generated from theengine 10, and a hot water supply tank 30 that uses the waste heat fromthe waste heat recovery apparatus 20.

The electric generator 2 and the engine 10 are installed in the insideof an engine room E of a chassis formed apart from the heat demandplaces 30.

The electricity generated at the electric generator 2 is supplied to thehome appliances such as the various kinds of illuminators and the heatpump type air conditioner 4 and etc.

The heat pump type air conditioner 4 comprises a compressor 5, a 4-wayvalve 6, an indoor heat exchanger 7, an expanding apparatus 8, and anoutdoor heat exchanger 9.

The refrigerant compressed in the compressor 5 is circulated to thecompressor as passing the 4-way valve 6, the outdoor heat exchanger 9,the expanding apparatus 8, indoor heat exchanger 7 and the 4-way valve 6in sequence when the heat pump type air conditioner 4 is in a coolingoperation, therefore, the outdoor heat exchanger 9 operates as acondenser and the indoor heat exchanger 7 operates as an evaporator takethe heat from indoor air.

On the other hand, as the refrigerant compressed in the compressor 5 iscirculated to the compressor as passing the 4-way valve 6, the indoorheat exchanger 7, the expanding apparatus 8, outdoor heat exchanger 9,and the 4-way valve 6 in sequence when the heat pump type airconditioner 4 is in a heating operation, therefore, outdoor heatexchanger 9 operates as a evaporator and the indoor heat exchanger 7operates as a condenser warm the indoor air.

The waste heat recovery apparatus 20 comprises an exhaust gas heatexchanger 22 taking the heat of the exhaust gas exhausted from theengine 10 and a cooling water heat exchanger 24 taking the heat of thecooling water used to cool the engine 10.

The exhaust gas heat exchanger 22 is connected with the hot water supplytank 30 and a first heat supply line 23, and the waste heat took fromthe exhaust gas of engine is transferred to the hot water supply tank 30through the first heat supply line 23.

The cooling water heat exchanger 24 is connected with the hot watersupply tank 30 and a second heat supply line 25, and the heat took fromthe cooling water used to cool the engine 10 is transferred to the hotwater supply tank 30 through the second heat supply line 25.

The hot water supply is connected with the hot water supply tank 30.

The water supplied through a water supply path 32 is discharged into awater discharge path 34 after boiled in the inside of the hot watersupply tank 30 as the water supply path 32 through which the water issupplied from outside and the discharge path 34 discharging the waterheated in the hot water supply tank 30 are connected with the hot watersupply tank 30.

The efficiency of the co-generation according to the conventional artcannot be maximized because the waste heat of the engine 10 is not usedin the heat pump type air conditioner 4, but only used for supplying thehot water.

SUMMARY OF THE INVENTION

The present invention is contrived to overcome the above-mentionedconventional problems, and an object of the present invention is toprovide a co-generation and control method of the same increasing thehot water supply efficiency by transferring the waste heat of the drivesource to the cold water supplied from outside and the hot watersupplied from the hot water storage tank or to one of them selectivelyand maximizing the hot water supply efficiency while minimizing thepower consumption of the air conditioner.

The co-generation according to the present invention to achieve theabove-mentioned object comprises a hot water supply heat exchangerheating water; a heat transfer path connected with the hot water supplyheat exchanger for transferring heat; a hot water storage tank connectedwith the hot water supply heat exchanger and the water circulation path;a hot water storage pump installed at the water circulation path; awater supply path connected with the water circulation path; a watersupply pump installed at the water supply path; a hot water supply heatexchanger bypassing path formed at the water circulation path; and a hotwater supply heat exchanger bypassing valve controlling the watercirculation path and the hot water supply heat exchanger bypassing path.

The co-generation further comprises a hot water storage temperaturesensor gauging the temperature of the water supplied to the watercirculation path from the hot water storage tank; water boil recoveryentrance temperature sensor gauging the temperature of the waterstreaming into the hot water supply heat exchanger; water boil entrancetemperature sensor gauging the temperature of the heat medium streaminginto the hot water supply heat exchanger through the heat transfer path;and a control unit controlling the water supply pump, the water storagepump, and the hot water supply heat exchanger bypassing valve inaccordance with the perceived temperature by the hot water storagetemperature sensor, the water boil recovery entrance temperature sensor,and the water boil entrance temperature sensor.

The co-generation further comprises an electric generator; a drivesource operating the electric generator; and a waste heat recovery heatexchanger recovering the waste heat of the drive source and connectedwith the heat transfer path.

The co-generation according to the present invention comprises anelectric generator; a drive source operating the electric generator; awaste heat recovery heat exchanger recovering the waste heat from thedrive source; a hot water supply heat exchanger installed to heat thewater; an air conditioner air-conditioning the indoor air; a supplyingheat exchanger installed at the refrigerant path of the air conditioner;a heat transferring path connecting the waste heat recovery heatexchanger, the hot water supply heat exchanger, and the supplying heatexchanger; a hot water storage tank connected with the hot water supplyheat exchanger and the water circulation path; a water supply pathconnected with the water circulation path; and a hot water supply heatexchanger bypassing apparatus for bypassing of the water supplied to thewater circulation path from the hot water storage tank through the hotwater supply heat exchanger.

The air conditioner is a heat pump type air conditioner including acompressor, a 4-way valve, an outdoor heat exchanger, an expandingapparatus, and an indoor heat exchanger.

The heat pump type air conditioner further includes the outdoor heatexchanger bypassing apparatus for bypassing of the refrigerant throughthe outdoor heat exchanger.

The supplying heat exchanger is installed at the refrigerant pathbetween the 4-way valve and the outdoor heat exchanger.

The co-generation further comprises a hot water supply heat exchangerbypassing apparatus for bypassing of the heat of the waste heat recoveryheat exchanger through the hot water supply heat exchanger; and asupplying heat exchanger bypassing apparatus for bypassing of the heatof the waste heat recovery heat exchanger through the supplying heatexchanger.

The co-generation further comprises an exhausting heat exchangerexhausting the heat to outside as installed between the hot water supplyheat exchanger and the supplying heat exchanger on the heat transferencepath; a hot water supplying/exhausting heat exchanger bypassingapparatus for bypassing of the heat of the waste heat recovery heatexchanger through the hot water supply heat exchanger and the exhaustingheat exchanger; an exhausting heat exchanger bypassing apparatus forbypassing of the heat of the heat of the waste heat recovery heatexchanger through the exhausting heat exchanger; and a supplying heatexchanger bypassing apparatus for bypassing of the heat of the wasteheat recovery heat exchanger through the supplying heat exchanger.

A check valve is installed at the water supply path.

The water supply path is connected with the reservoir.

The co-generation further comprises a hot water storage tank watersupply apparatus supplying water in the hot water storage tank to thewater circulation path; and a water supply apparatus supplying water tothe water supply path.

The hot water supply heat exchanger bypassing apparatus includes a hotwater supply heat exchanger bypassing path formed at the watercirculation path; and a hot water supply heat exchanger bypassing valvecontrolling the hot water supply heat exchanger bypassing path.

A check valve is installed between the hot water storage tank and thehot water supply heat exchanger bypassing valve at the water circulationpath.

The co-generation further comprises a hot water storage tank temperaturesensor gauging the temperature of the water supplied to the watercirculation path from the hot water storage tank; a water boil recoveryentrance temperature sensor gauging the temperature of the waterstreaming into the hot water supply heat exchanger; a water boilentrance temperature sensor gauging the temperature of the heat mediumstreaming into the hot water supply heat exchanger through the heattransfer path; and a control unit controlling the water supplyapparatus, the hot water storage tank water supply apparatus, and thehot water supply heat exchanger bypassing valve in accordance with theperceived temperature by the hot water storage tank temperature sensor,the water boil recovery entrance temperature sensor, and the water boilentrance temperature sensor.

The hot water storage tank water supply apparatus is a hot water storagetank pump installed at the water circulation path, and the water supplyapparatus is composed of a water supply pump installed at the watersupply path.

The control method of the co-generation according to the presentinvention drives the water supply pump and the hot water storage pump,and controls the hot water supply heat exchanger bypassing valve to be ahot water supply heat exchanger supply mode when the temperature of thehot water storage tank is the first set point more than the temperatureof the water boil recovery entrance and the temperature of the waterboil entrance is the second set point more than the temperature of thehot water storage tank.

The control method of the co-generation according to the presentinvention drives the water supply pump and the hot water storage tankpump, and controls the hot water supply heat exchanger bypassing valveto be a hot water supply heat exchanger by passing mode when thetemperature of the hot water storage tank is the First set point morethan the temperature of the water boil recovery entrance and thetemperature of the water boil entrance is not the second set point morethan the temperature of the hot water storage tank.

The control method of the co-generation according to the presentinvention drives the hot water storage tank pump as well as stopsoperating the water supply pump, and controls the hot water supply heatexchanger bypassing valve to be a hot water supply heat exchanger supplymode when the temperature of the hot water storage tank is not the Firstset point more than the temperature of the water boil recovery entranceand the temperature of the water boil entrance is the second set pointmore than the temperature of the hot water storage tank.

The control method of the co-generation according to the presentinvention drives the hot water storage tank pump as well as stopsoperating of the water supply pump, and controls the hot water supplyheat exchanger bypassing valve to be a hot water supply heat exchangerbypassing mode when the temperature of the hot water storage tank is notthe first set point more than the temperature of the water boil recoveryentrance and the temperature of the water boil entrance is not thesecond set point more than the temperature of the hot water storagetank.

The co-generation and the control method of the same according to thepresent invention composed as above are advantageous that the effectivewater boil heat is increased as supplying the cold water supplied fromthe water supply and the hot water supplied from the hot water storagetank to the properly to the hot water supply heat exchanger, and heatexchange it with the heat medium such as an anti freezing solutionpassing through the hot water supply heat exchanger.

BRIEF DESCRIPTION OF THE DRAWING

FIG. 1 is a block diagram of the co-generation according to theconventional art,

FIG. 2 is a block diagram illustrating the air conditioner of anembodiment of the co-generation according to the present inventionoperating for air-cooling and under water boil mode,

FIG. 3 is a block diagram illustrating the air conditioner of anembodiment of the co-generation according to the present inventionoperating for air-cooling under the not water boil mode,

FIG. 4 is a block diagram illustrating the condition that the airconditioner of an embodiment of the co-generation according to thepresent invention operates for air heating under the outdoor fan controlmode and the water boil mode,

FIG. 5 is a block diagram illustrating the air conditioner of anembodiment of the co-generation according to the present inventionoperating for air heating under the low-pressure control mode and thewater boil mode,

FIG. 6 is a block diagram illustrating the air conditioner of anembodiment of the co-generation according to the present inventionoperating for air heating under the maximum supply mode and the notwater boil mode,

FIG. 7 is a magnified view of the water boil unit of an embodiment ofthe co-generation according to the present invention under the watersupply and heat accumulation water boil mode,

FIG. 8 is a magnified view of the water boil unit of an embodiment ofthe co-generation according to the present invention under the watersupply and water boil mode,

FIG. 9 is a magnified view of the water boil unit of an embodiment ofthe co-generation according to the present invention under the heataccumulation mode,

FIG. 10 is a magnified view of the water boil unit of an embodiment ofthe co-generation according to the present invention under thecirculation mode,

FIG. 11 is a block diagram of another embodiment of the co-generationaccording to the present invention.

DETAILED DESCRIPTION OF THE INVENTION

Reference will now be made in detail hereinafter as for theco-generation and the control method of the same in accordance with thepresent invention with reference to the accompanying drawings.

FIG. 2 is a block diagram illustrating the air conditioner of anembodiment of the co-generation according to the present inventionoperating for air-cooling and under water boil mode, FIG. 3 is a blockdiagram illustrating the air conditioner of an embodiment of theco-generation according to the present invention operating forair-cooling under the not water boil mode, FIG. 4 is a block diagramillustrating the condition that the air conditioner of an embodiment ofthe co-generation according to the present invention operates for airheating under the outdoor fan control mode and the water boil mode, FIG.5 is a block diagram illustrating the air conditioner of an embodimentof the co-generation according to the present invention operating forair heating under the low-pressure control mode and the water boil mode,and FIG. 6 is a block diagram illustrating the air conditioner of anembodiment of the co-generation according to the present inventionoperating for air heating under the maximum supply mode and the notwater boil mode.

The co-generation according to the present embodiment comprises an airconditioner 50 air-conditioning the indoor, a hot water supply heatexchanger 70 boiling water, an electric generator 110 generatingelectricity, a drive source 120 operating the electric generator 110 andgenerating heat, and a waste heat recovery heat exchanger 130 recoveringthe waste heat of the drive source 120 as illustrated in FIGS. 2 to 6.

It is possible for the air conditioner 50 to be composed of a heat pumptype air conditioner including a compressor 52, a 4-way valve 54, anindoor heat exchanger 56, expansion apparatus 58 and 59, and an outdoorheat exchanger 60, and also possible to be composed of an exclusiveair-cooling air conditioner including a compressor 52, an indoor heatexchanger 56, an expanding apparatus 58 and 59, and an outdoor heatexchanger 60, but not including the 4-way valve. The reference will nowbe made in detail as limited to the air conditioner composed of the heatpump type air conditioner on the following.

As the heat pump type air conditioner is composed of an outdoormachinery O and an indoor machinery I, it is possible that an indoormachinery I is connected with an outdoor machinery O, also possible thatplural indoor machineries I are connected in a row with an outdoormachinery O, also possible that plural outdoor machineries O areconnected in a row each other, and also possible that plural indoormachineries I are connected in a row each other.

The compressor 52, the 4-way valve 54, the indoor heat exchanger 56, theexpansion apparatus 58, and the outdoor heat exchanger 60 are connectedwith the refrigerant laying pipe 61, a refrigerant flowing path.

An accumulator 53 in which the liquid refrigerant a part of refrigerantis accumulated is installed at the suction pipe through which therefrigerant is inhaled in the compressor 52.

The 4-way valve 54 controls the inner path for flowing the refrigerantcompressed at the compressor 52 to the indoor heat exchanger 56 asillustrated in FIGS. 4 to 6 when the air heating operation of the heatpump type air conditioner 50, and controls the inner path for flowingthe refrigerant compressed at the compressor 52 to the outdoor heatexchanger 60 as illustrated in FIGS. 2 and 3 when the air-coolingoperation of the heat pump type air conditioner 50.

An indoor fan 57 sending indoor air to the indoor heat exchanger 56 isinstalled beside the indoor heat exchanger 56.

The expansion apparatus 58 and 59 are described as limited to becomposed of a vessel or a linear expansion valve.

The expansion apparatus 58 and 59 include an indoor expansion valve 58controlling each amount of the refrigerant of the each indoor machineryI as installed at the indoor machinery I, and an outdoor expansion valve59 expanding the refrigerant while the air heating operation asinstalled at the outdoor machinery O.

An outdoor fan 61 sending the outdoor air to the outdoor heat exchanger60 is installed beside the outdoor heat exchanger 60.

The compressor 52, 4-way valve 54, outdoor expansion valve 59, and theoutdoor heat exchanger 60 are installed at the outdoor machinery O.

The indoor heat exchanger 56 and the indoor expansion valve 58 areinstalled at the indoor machinery I.

The compressor 52, indoor fan 57, and the outdoor fan 61 of the heatpump type air conditioner 50 are operated by electricity generated bythe electric generator 110.

The heat pump type air conditioner 50 further includes an outdoor heatexchanger bypassing apparatus 62 for bypassing of the refrigerantthrough the outdoor heat exchanger 60.

The outdoor heat exchanger bypassing apparatus 62 includes an outdoorheat exchanger bypassing path 63 that an end is connected with therefrigerant path connected with the inlet of the outdoor heat exchanger60 and the other end is connected with the refrigerant path connectedwith the outlet of the outdoor heat exchanger for bypassing of therefrigerant passed through the supply heat exchanger 68 described on thefollowing while the air-cooling operation as illustrated in FIGS. 2 and3 through the outdoor heat exchanger 60, and for bypassing of therefrigerant expanded at the indoor expansion valve 58 while the airheating operation through the outdoor heat exchanger 60 as illustratedin FIGS. 5 and 6.

The outdoor expansion valve 59 is installed at the outdoor heatexchanger bypassing path 63.

An outdoor expansion valve bypassing path 64A is formed at the outdoorheat exchanger bypassing path 63 for bypassing of the refrigerant flowninto the outdoor heat exchanger bypassing path 63 through the outdoorexpansion valve 59 during the air-cooling operation of the heat pumptype air conditioner 50 as illustrated FIGS. 2 and 3.

A check valve 64B passing the refrigerant during the air-coolingoperation and passing the refrigerant through the outdoor expansionvalve 59 as blocked during the air heating operation of the heat pumptype air conditioner 50 is installed at the outdoor expansion valvebypassing path 64A.

An outdoor heat exchanger bypassing path opening and shutting valve 54Copening and shutting the outdoor heat exchanger bypassing path 63 isinstalled at the outdoor heat exchanger bypassing path 63.

The outdoor heat exchanger bypassing apparatus 62 includes the outdoorheat exchanger opening and shutting valve 65A installed at therefrigerant path connected with the outlet of the outdoor heat exchanger60 during the air heating operation.

The outdoor heat exchanger bypassing apparatus 62 further includes aconnection path 66A connecting the refrigerant path connected with theinlet of the outdoor heat exchanger 60 and the outdoor heat exchangerbypassing path 63 during the air heating operation, and a connectionpath opening and shutting valve 66B opening and shutting the connectionpath 66A.

A check valve 65B preventing the streaming of the refrigerant into theoutdoor heat exchanger 60 without passing through the outdoor expansionvalve 59 during the air heating operation of the heat pump type airconditioner is installed at the refrigerant path connected with theinlet of the outdoor heat exchanger 60 of the outdoor heat exchangerbypassing apparatus 62.

Here, the outdoor heat exchanger bypassing apparatus 62, as illustratedin FIGS. 2 and 3, opens the outdoor heat exchanger bypassing pathopening and shutting valve 64C as well as shutting the outdoor heatexchanger opening and shutting valve 65A during the air-coolingoperation, shutting the connection path opening and shutting valve 66B,and the refrigerant bypasses the outdoor expansion valve 59 as well asby passing the outdoor heat exchanger 60.

The outdoor heat exchanger bypassing apparatus 62, as illustrated inFIG. 4, shuts the outdoor heat exchanger bypassing path opening andshutting valve 64C as well as opening the outdoor heat exchanger openingand shutting valve 65A during the outdoor fan control air heatingoperation, opening the connection path opening and shutting valve 66B,and the refrigerant passes through the outdoor heat exchanger 60 afterpassing through the outdoor expansion valve 59.

The outdoor heat exchanger bypassing apparatus 62, as illustrated FIGS.5 and 6, opening the outdoor heat exchanger bypassing path opening andshutting valve 64C as well as shutting the outdoor heat exchangeropening and shutting valve 65A during the lo-pressure control airheating operation and maximum supply air heating operation, shutting theconnection path opening and shutting valve 66B, and the refrigerantbypasses the outdoor heat exchanger 60 after passing through the outdoorexpansion valve 59.

Meanwhile, the co-generation further comprises a supply heat exchanger68 installed on the refrigerant path of the heat pump type airconditioner 50 for transferring the waste heat recovered from the wasteheat recovery heat exchanger 130 as a refrigerant of the heat pump typeair conditioner 50, and transferring the heat transferred from therefrigerant of the heat pump type air conditioner 50 to the hot watersupply heat exchanger 70 if necessary.

The supply heat exchanger 69 is installed on the refrigerant pathbetween the 4-way valve 54 and the outdoor heat exchanger 60.

That is, the supply heat exchanger 68 may be operated as a condensercondensing the refrigerant during the air-cooling operation of the heatpump type air conditioner 50, and also may be operated as a evaporatorevaporating the refrigerant during the air heating operation of the heatpump type air conditioner 50.

A water boil unit 78 boiling cold water or hot water as supplying to thehot water supply heat exchanger 70 is connected with the hot watersupply heat exchanger 70.

The water boil unit 78 includes a hot water storage tank 80accommodating water, and a water circulation path 81 connecting the hotwater storage tank 80 and the hot water supply heat exchanger 70.

The hot water storage tank 80 is a kind of heat store tank storing theheat recovered from the hot water supply heat exchanger 70, and thewater circulation path 81 is formed as the water of the hot waterstorage tank 80 is circulated through the inside of the hot waterstorage tank 80 after supplied to the hot water supply heat exchangerand passed through the hot water supply heat exchanger 70.

A hot water storage tank water supply apparatus 82 supplying the waterin the inside of the hot water storage tank 80 to the water circulationpath 82 is installed at the water circulation path 82.

The hot water storage tank water supply apparatus 82 is composed of ahot water storage tank pump installed at the water circulation path 81for pumping the water in the hot water storage tank 80 to be circulatedto the hot water storage tank 80 after passing through the hot watersupply heat exchanger 70.

On the other hand, a water supply path 83 supplying outside water to thewater circulation path 82 is connected with the water circulation path81.

The water supply path 83 is capable of supplying water from the watersupply service to the water circulation path 81 as directly connectedwith the water supply service and also capable of supplying water fromthe water supply tank 84 to the water circulation path 81 as connectedwith a separate water supply tank 84, and the water supply path 83 willnow be described as limited to the water supply path 83 connected withthe water supply tank 84 on the following.

A check valve 85 preventing flowing backward of water in the watercirculation path 81 through the water supply path 83 and a water supplyapparatus 86 pumping water in the water supply tank 84 to the watersupply path 83 are installed at the water supply path 83.

The water supply apparatus 86 is composed of a water supply pumpinstalled at the water supply path 83, especially between the watersupply tank 84 and the check valve 85.

A hot water supply heat exchanger bypassing apparatus for bypassing ofthe water supplied to the water circulation path 81 from the hot waterstorage tank 80 through the hot water supply heat exchanger 130 isinstalled at the water circulation path 81.

The hot water supply heat exchanger bypassing apparatus includes a hotwater supply heat exchanger bypassing path 87 formed at the watercirculation path 81; and a hot water supply heat exchanger bypassingvalve 88 controlling the water circulation path 81 and the hot watersupply heat exchanger bypassing path 87.

The hot water supply heat exchanger bypassing valve 88 decides thebypassing of the hot water supply heat exchanger of the water suppliedfrom the hot water storage tank 80 as installed at the diverging part ofthe water circulation path 87 and the hot water supply heat exchangerbypassing path 87.

The hot water supply heat exchanger bypassing valve 88 has a hot watersupply heat exchanger bypassing mode bypassing the water supplied fromthe hot water storage tank 80 through the hot water supply heatexchanger 70 during the water supplying and boil mode and thecirculation mode described on the following, and has a hot water supplyheat exchanger supply mode bypassing the water supplied from the hotwater storage tank 80 through the hot water supply heat exchanger 70during the water supplying and heat storing water boil mode and the heatstoring mode described on the following.

On the other hand, a check valve 89 is installed between the hot waterstorage tank pump 82 and hot water supply heat exchanger bypassing valve88 at the water circulation path 81.

The electric generator 110 supplying electricity to electronic machinerysuch as heat pump type air conditioner 50 or various illuminations andetc generates electricity when the output shaft is rotated as a rotor,as an alternator or a direct current generator, is connected with theoutput shaft of the drive source 120.

The electric generator 110 supplies generated electricity through thepower line 111 as connected with the heat pump type air conditioner 50and etc by power line 111.

The drive source 120 is composed of a fuel cell or an engine operated asusing gas, petroleum, or fossil fuel, and it is described as limited tothe engine on the following.

A fuel inlet 121 into which the fuel such as gas, petroleum and etc arepoured, an inlet 122 through which the air is inhaled from outside tothe engine 120, and an exhaust pipe 123 through which the waste gasexhausted from the engine 120 passes are installed at the engine 120.

The waste heat recovery heat exchanger 130 is composed of a coolant heatexchanger 132 recovering the coolant heat of the engine as connectedwith the engine through the coolant line 124, and a exhaust gas heatexchanger 134 installed on the exhaust pipe 123 to recover the waste gasheat exhausted from the engine 120.

A coolant circulation pump 125 circulating the coolant through theengine 120 and the coolant heat exchanger 132 is installed at the engine120 or the coolant line 124.

The electric generator 110, engine 120, and the waste heat recovery heatexchanger 130 are installed at the engine unit EN.

The co-generation comprises a heat transferring apparatus 150transferring the heat of the heat of the exhaust gas exchanger 130 tothe heat demand places such as the hot water supply heat exchanger 70,the air conditioner and etc.

Here, the heat transferring apparatus 150 may transfer the heat of thewaste heat recovery heat exchanger only to the hot water supply heatexchanger 70 and the heat pump type air conditioner 50, may transfer theheat of the heat of the waste heat recovery heat exchanger 130 to thehot water supply heat exchanger 70 and the heat pump type airconditioner 50, and may transfer the heat of the heat pump type airconditioner 50 to the hot water supply heat exchanger if necessary.

As the hot water supply efficiency of the heat transferring apparatus150 is maximized when the heat of the refrigerant is transferred to thehot water supply heat exchanger 70 during the air-cooling operation ofthe heat pump type air conditioner 50, the heat transferring apparatus150 is described as limited that the heat of the waste heat recoveryheat exchanger 130 is transferred to the hot water supply heat exchanger70 and the heat pump type air conditioner 50, and the heat of the heatpump type air conditioner 50 is transferred to the hot water supply heatexchanger 70, if necessary.

The heat transferring apparatus 150 includes a heat transfer path 170connecting the heat of the waste heat recovery heat exchanger 130, hotwater supply heat exchanger 70, radiant heat exchanger 160, and thesupply heat exchanger 68.

Here, as the radiant heat exchanger 160 exhausts the entire of a portionof the heat recovered from the waste heat recovery heat exchanger 130 tooutside if necessary, a radiant heat fan 162 sending the outside air tothe radiant heat exchanger 160 is installed beside the radiant heatexchanger 160.

A heat medium circulation pump 172 circulating the heat medium such asan anti freezing solution (hereinafter referred to as “heat medium”)through the waste heat recovery heat exchanger 130, water heat exchanger70, radiant heat exchanger 160, and the supply heat exchanger 68 isinstalled at the heat transfer path 170.

As the heat transfer apparatus 150 transfers the heat recovered from theengine 120 the most suitably in accordance with the water boil,air-cooling/air warming, and the condition of the outdoor temperaturewhen the heat recovered from the engine, the heat medium passed throughthe waste heat recovery heat exchanger 130, bypasses at least one of thehot water supply heat exchanger 70, radiant heat exchanger 160, and thesupply heat exchanger 68, it is described as limited that the heatmedium passed through the waste heat recovery heat exchanger 130bypasses through each of the heat exchanger 70, 160, and 68 on thefollowing.

The heat transfer apparatus 150 further includes the hot watersupply/radiant heat exchanger bypassing apparatus 180 formed forbypassing of the heat of the waste heat recovery heat exchanger 130through the hot water supply heat exchanger and the radiant heatexchanger.

The water boil/radiant heat exchanger bypassing apparatus 180 includes awater boil/radiant heat exchanger bypassing path 182 formed at the heattransfer path 170; and a water boil/radiant heat exchanger bypassingvalve 184 installed at the diverging point of the water boil/radiantheat exchanger bypassing path 182 and the heat transfer path 170.

The heat transfer apparatus 150 further includes a radiant heatexchanger bypassing apparatus 190 bypassing the heat of the waste heatrecovery heat exchanger 130 through the radiant heat exchanger 160.

The radiant heat exchanger bypassing apparatus 190 includes a radiantheat exchanger bypassing path 192 formed at the heat transfer path 170;and a radiant heat exchanger bypassing valve 194 installed at thediverging point of the radiant heat exchanger bypassing path 192 and theheat transfer path 170.

The heat transfer apparatus 150 further includes a supply heat exchangerbypassing apparatus 200 bypassing the heat of the waste heat recoveryheat exchanger 130 through the supply heat exchanger 68.

The supply heat exchanger bypassing apparatus 200 includes a supply heatexchanger bypassing path 202 formed at the heat transfer path 170; and asupply heat exchanger bypassing valve 204 installed at the divergingpoint of the supply heat exchanger bypassing path 202 and the heattransfer path 170.

Both of the hot water supply heat exchanger 70 and the radiant heatexchanger 160 are installed at the radiant unit EX of the co-generation.

All of the water boil/radiant heat exchanger bypassing path 182, thewater boil/radiant heat exchanger bypassing valve 184, the radiant heatexchanger bypassing path 192, the radiant heat exchanger bypassing valve194, the supply heat exchanger bypassing path 202, and the supply heatexchanger bypassing valve 204 are installed at the radiant heat unit EXof the co-generation.

The co-generation further comprises a control unit 210 controlling thewater boil/radiant heat exchanger bypassing valve 184, the radiant heatexchanger bypassing valve 194, the supply heat exchanger bypassing valve204, the outdoor heat exchanger opening and shutting valve 65A, theoutdoor heat exchanger bypassing path opening and shutting valve 64C,and the connection path opening and shutting valve 66B in accordancewith the air-cooling/air warming and water boiling of the heat pump typeair conditioner 50.

The control unit 210 is composed of a master PCB 212 installed at theengine unit EN, and a slave PBC 214 installed at the radiant heat unitEX and connected with the master PBC 212 by a control line.

The various kinds of sensors perceiving the temperature or the flux areinstalled at the co-generation.

The co-generation comprises an intake port temperature sensor 220composed of a thermistor perceiving the temperature of outside airinhaled into the intake port 12, a coolant heat exchanger outlettemperature sensor 222 composed of a thermistor perceiving thetemperature of the outlet of the coolant heat exchanger 132 of the heattransfer path 170, a waste gas heat exchanger outlet temperature sensor224 composed of a thermistor 224A and RTD sensor 224B perceiving thetemperature of the outlet of the waste gas heat exchanger 134 of theheat transfer path 170, and an exhaust pipe temperature sensor 226composed of RTD sensors 226A, 226B perceiving the each temperature offront and rear of the waste gas heat exchanger 134 of the exhaust pipe123.

The intake port temperature sensor 220, the coolant heat exchangeroutlet temperature sensor 222, the waste gas heat exchanger outlettemperature sensor 224, and the exhaust pipe temperature sensor 226 areinstalled at the inside of the engine unit EN.

The co-generation comprises the No. 1 transfer path temperature sensor230 perceiving the before temperature of the heat medium circulationpump 172 of the heat transfer path 170 and the No. 2 heat transfer pathtemperature sensor 232 perceiving the temperature between the radiantheat exchanger bypassing path 192 and the radiant heat exchangerbypassing valve 204 of the heat transfer path 170.

The No. 1 heat transfer path temperature sensor 230 and the No. 2 heattransfer path temperature sensor 232 are installed at the radiant heatunit EX.

The radiant heat unit EX is connected with the tank connection path 252that an expansion tank 250 is connected between the heat mediumcirculation pump 172 and the supply heat exchanger bypassing path 202 ofthe heat transfer path 170.

Reference will now be made in detail as for the operation of the presentinvention configured as above.

First, when the engine 120 is operated, the electric generator 110generates electricity as the rotor is rotated, and the generatedelectricity is supplied to the heat pump type air conditioner 50 throughthe power line 111 as illustrated in FIGS. 2 to 5.

The exhaust gas heat and the coolant heat of the engine are recovered atthe waste heat recovery heat exchanger 130, the coolant heat exchanger132 and the exhaust gas heat exchanger 134 during the operation of theengine 120.

The co-generation controls the bypassing of the refrigerant through theoutdoor heat exchanger 60 as well as operating the heat pump type airconditioner 50 to be an air-cooling mode when the heat pump typeair-conditioner 50 is required of air-cooling and water boiling, andcontrols the heat medium of the heat transfer path 170 to be circulatedthrough the waste heat recovery heat exchanger 130, hot water supplyheat exchanger 70, and the supply heat exchanger 68.

The heat pump type air conditioner 50 controls the 4-way valve 54 to bean air-cooling mode as well as operating the compressor 52, opens theoutdoor heat exchanger bypassing path opening and shutting valve 64C aswell as shutting the outdoor heat exchanger opening and shutting valve65A, and shuts the connection path opening and shutting valve 66B.

As describing the flowing of the refrigerant of the heat pump type airconditioner 50, the high temperature and high pressure refrigerantcompressed at the compressor 52 is supplied to the supply heat exchanger68 as passing through the 4-way valve 54, condensed as taken the heataway from the supply heat exchanger 68 when it passes through the supplyheat exchanger 68, and bypasses the outdoor heat exchanger 60 afterthat.

The refrigerant bypassed the outdoor heat exchanger 60 is evaporated astransferred to the indoor heat exchanger 56 after transferred to theindoor machinery I and expanded at the indoor expansion valve 58, andafter that, circulated to the compressor 52 through the 4-way valve 54as transferred to the outdoor machinery O.

That is, the refrigerant of the heat pump type air conditioner iscondensed at the supply heat exchanger 68, and cooling the indoor air asevaporated at the indoor heat exchanger 56.

On the other hand, the control unit 210 controls the water boil/radiantheat exchanger bypassing valve 184 to be the water boil/radiant heatsupply mode as well as operating the heat medium circulation pump 172for circulation of the heat medium of the heat transfer path 170 throughthe waste heat recovery heat exchanger 130, hot water supply heatexchanger 70, and the supply heat exchanger 68, and controls the supplyheat exchanger bypassing valve 204 to be the supply heat exchanger mode.

At this time, as the control unit 210 controls the radiant heatexchanger bypassing valve 194 in accordance with the temperature of theheat medium, it controls the radiant heat exchanger bypassing valve 194to be the radiant heat exchanger supply mode and when the temperature ofthe heat medium is over the set point, and it controls the radiant heatexchanger bypassing valve 194 to be the bypassing mode when thetemperature of the heat medium is not more than the set point.

As describing the flow of the heat medium in the heat transfer path 170,the heat medium in the heat transfer path 170 is heated as receiving theheat while passing through the waste heat recovery heat exchanger 130during the operation of the heat medium circulation pump 172, asillustrated in FIG. 2, and it streams into the water heat exchanger 70as passing through the water boil/radiant heat exchanger 130.

The heat medium flown into the hot water supply heat exchanger 70 heatsthe hot water supply heat exchanger 70 as transferring the heat to thewater boil exchanger 70, and after that, it passes through or bypassesthe radiant heat exchanger 160 in accordance with the temperaturecondition of the system.

The heat medium passed through or by passed the radiant heat exchanger160 is supplied as a supply heat exchanger 68 after passing through thesupply heat exchanger bypassing valve 204, the temperature of it israised by receiving heat from the high temperature and high pressurerefrigerant gas passing through the supply heat exchanger 68, and it iscirculated to the waste heat recovery heat exchanger 130.

That is, the water boiling capacity of the hot water supply heatexchanger 70 of the co-generation is improved as the refrigerant of theheat pump type air conditioner 50 is condensed as the heat is taken awayfrom the heat medium while passing through the supply heat exchanger,and as the heat of the waste heat recovery heat exchanger 130 and theheat of the supply heat exchanger 68 are transferred to the hot watersupply heat exchanger through the heat transfer path 170.

In the co-generation, the lower the temperature of the water supplied tothe hot water supply heat exchanger 70 from the water boiling unit 78,the larger the amount of the heat transference of the hot water supplyheat exchanger 70, and the heat medium passed through the hot watersupply heat exchanger 70 recovers a lot of heat from the refrigerantwhile passing through the supply heat exchanger 68, and the consumptionelectricity of the compressor is reduced compared with the sameair-cooling capacity of the heat pump type air conditioner 50.

The co-generation controls the refrigerant no to pass through theoutdoor heat exchanger 60 as well as operating the heat pump type airconditioner 50 to be air-cooling mode when the heat pump typeair-conditioner is under the air-cooling mode without request of waterboiling as illustrated in FIG. 3, and controls that the heat medium inthe heat transfer path 170 is circulated through the exhaust gas heatexchanger 130 and supply heat exchanger 68.

The heat pump type air conditioner 50 controls the 4-way valve 54 to bethe air-cooling mode as well as operating the compressor 52, opens theoutdoor heat exchanger bypassing path opening and shutting valve 64C aswell as shutting the outdoor heat exchanger opening and shutting valve65A, and shuts the connection path opening and shutting valve.

The co-generation operates the heat medium circulation pump 172 forcontrolling the heat medium in the heat transfer path 170 to becirculated through the waste heat recovery heat exchanger 130 and thesupply heat exchanger 68, controls the water boil/radiant heat exchangerbypassing valve 184 to be the water boil/radiant heat exchanger supplymode, controls the radiant heat exchanger bypassing valve 194 to be theradiant heat exchanger supply mode, and controls the supply heatexchanger bypassing valve 204 to be the supply heat exchanger supplymode.

As describing the flowing of the refrigerant of the heat pump type airconditioner 50, the high-temperature and high-pressure refrigerantcompressed at the compressor 52 is supplied to the supply heat exchangerpassed through the 4-way valve 54 and condensed as the heat is takenaway from the supply heat exchanger while passing the supply heatexchanger 68, and bypasses the outdoor heat exchanger 60.

The refrigerant bypassed the outdoor heat exchanger 60 is evaporated inthe indoor heat exchanger 56 after expanded in the expansion valve 58after transferred to the indoor machine I, and after that, transferredto the outdoor machine O and circulated to the compressor through the4-way valve 54.

That is, the refrigerant of the heat pump type air conditioner 50 iscondensed at the supply heat exchanger 68 and cools the indoor air asevaporated in the indoor heat exchanger 56.

As describing the flowing of heat medium of the heat transfer path 170,illustrated In FIG. 3, the heat medium in the heat transfer path 170 isboiled as receiving heat while passing through the waste heat recoveryheat exchanger 130 during the operation of the heat medium circulationpump 172, streams into the hot water supply heat exchanger 70 as passingthrough the water boil/radiant heat exchanger bypassing valve 184,streams into the radiant heat exchanger 192 after passing through thehot water supply heat exchanger 70, and radiates heat to outside aspassing through the radiant heat exchanger 192.

The heat medium radiated is supplied to the supply heat exchanger 68after passing through the supply heat exchanger bypassing valve 204, thetemperature of it gets higher as receiving heat from thehigh-temperature and high-pressure refrigerant gas passing through thesupply heat exchanger 68, and then, circulated to the exhaust gas heatexchanger 130.

That is, the water boiling capacity of the hot water supply heatexchanger 70 of the co-generation is improved as the refrigerant of theheat pump type air conditioner 50 is condensed as the heat of it istaken away from the heat medium while passing through the supply heatexchanger 68, and as the heat of the waste heat recovery heat exchanger130 and the heat of the supply heat exchanger 68 are transferred to thehot water supply heat exchanger 70 through the heat transfer path 170.

When the heat pump type air conditioner 50 is under the air warming modewithout water boiling request, as illustrated in FIG. 4, theco-generation passes the refrigerant through the outdoor heat exchanger60 as well as operating the heat pump type air-conditioner 50 to be airwarming mode, and controls the heat medium in the heat transfer path 170to be circulated through the waste heat recovery heat exchanger 130 andwater heat exchanger 70 or, as illustrated in FIG. 5, controls therefrigerant not to be circulated through the outdoor heat exchanger 60as well as operating the heat pump type air conditioner 50 to be the airwarming mode, and controls the heat medium in the heat transfer path 170to be circulated through the waste heat recovery heat exchanger 130, hotwater supply heat exchanger 70, and the supply heat exchanger 68.

It is desirable for the co-generation, as illustrated in FIG. 4, tomaximize the capacity of heat recovering to the hot water supply heatexchanger 70 and the capacity of water boiling as controlling therefrigerant to pass through the outdoor heat exchanger 60 and the heatmedium in the heat transfer path 170 to be circulated through the wasteheat recovery heat exchanger 130 and the water heat exchanger 70 whenthe outdoor temperature is not cold enough for the outdoor heatexchanger not frosted over, and it is desirable for the co-generation,as illustrated in FIG. 5, to prevent deterioration of the water boilingcapacity may be generated when the outdoor heat exchanger 60 is frostedover as stopping the passing of refrigerant through the outdoor heatexchanger 60 and controlling the heat medium in the heat transfer path170 to be circulated through the waste heat recovery heat exchanger 130,hot water supply heat exchanger 70, and the supply heat exchanger 68.

Reference will now be made in detail to the case passing the refrigerantto the outdoor heat exchanger 60 as well as operating the heat pump typeair conditioner 50 to be the air warming mode controlling the heatmedium in the heat transfer path 170 to be circulated through the wasteheat recovery heat exchanger 130 and the hot water supply heat exchanger70, as illustrated in FIG. 4.

The heat pump type air conditioner 50 controls the 4-way valve to be theair-warming mode as well as operating the compressor 52, shuts theoutdoor heat exchanger bypassing path opening and shutting valve 65C aswell as opening the outdoor heat exchanger opening and shutting valve65A, and opens the connection path opening and shutting valve 66B.

As, describing the flowing of refrigerant in the heat pump type airconditioner 50, the high-temperature and high-pressure refrigerantcompressed at the compressor 52 passes through the 4-way valve 54 andtransferred to the indoor machine I, condensed while passing through theindoor heat exchanger 60 of the indoor machine I, and expanded whilepassing through the indoor expansion valve 58.

The refrigerant expanded at the indoor expansion valve 58 is transferredto the outdoor machine O and expanded again while passing through theoutdoor expansion valve 59, and streams into the outdoor heat exchanger60.

The refrigerant flown into the outdoor heat exchanger 60 evaporatedwhile passing through the outdoor heat exchanger 60, passes through thesupply heat exchanger 68 without heat exchanging, and circulated to thecompressor 52 after passing through the 4-way valve 54.

That is, the refrigerant in the heat pump type air conditioner warmsindoor as condensed at the indoor heat exchanger 56 and evaporated atthe outdoor heat exchanger 60.

The control unit 210 controls the water boil/radiant heat exchangerbypassing valve 184 to be the water boil/radiant heat exchanger supplymode as well as operating the heat medium circulation pump 172 tocirculate the heat medium in the heat transfer path 170 through thewaste heat recovery heat exchanger 130 and the hot water supply heatexchanger 70, and controls the supply heat exchanger bypassing valve 204to be the supply heat exchanger bypassing mode.

As the control unit 210 controls the radiant heat exchanger bypassingvalve 194 in accordance with the temperature, it controls the radiantheat exchanger bypassing valve 194 to be the radiant heat exchangersupply mode when the temperature of the heat medium is over the setpoint, and controls the radiant heat exchanger bypassing valve 194 to bethe bypassing mode when the temperature is not more than the set point.

As describing the flowing of the heat medium in the heat transfer path170, the heat medium in the heat transfer path 170 is heated asreceiving heat while passing through the waste heat recovery heatexchanger 130 during the operation of the heat medium circulation pump172, illustrated in FIG. 4, and streams into the hot water supply heatexchanger 70 as passing through the water boil/radiant heat exchangerbypassing valve 184.

The heat medium flown into the hot water supply heat exchanger 70 heatsthe hot water supply heat exchanger as transferring heat to the hotwater supply heat exchanger 70, and passes through or bypasses theradiant heat exchanger 160 in accordance with the temperature conditionand etc of the system.

The heat medium passed through or bypassed the radiant heat exchanger160 bypasses the supply heat exchanger 68 after passing through thesupply heat exchanger bypassing valve 204, and circulated through thewaste heat recovery heat exchanger 130.

That is, the water boiling capacity of the hot water supply heatexchanger 70 of the co-generation is improved as the heat of the wasteheat recovery heat exchanger 130 is transferred to the water heatexchanger 70 through the heat transfer path 170.

Reference will now be made in detail to the case not passing therefrigerant to the outdoor heat exchanger 60 as well as operating theheat pump type air conditioner 50 to be the air warming mode andcontrolling the heat medium in the heat transfer path 170 to becirculated through the waste heat recovery heat exchanger 130, hot watersupply heat exchanger 70, and the supply heat exchanger 68.

The heat pump type air conditioner 50 controls the 4-way valve 54 to bethe air warming mode as well as operating the compressor 52, and openingthe outdoor heat exchanger bypassing valve 65 as well as shutting theoutdoor heat exchanger bypassing valve 64 and the connection pathopening and shutting valve 67.

As describing the flowing of the refrigerant of the heat pump type airconditioner 50, the high-temperature and high-pressure refrigerantcompressed at the compressor 52 is transferred to the indoor machine Ias passing through the 4-way valve, condensed while passing through theindoor heat exchanger 60 of the indoor machine I, and expanded whilepassing through the indoor expansion valve 58.

The refrigerant expanded at the indoor expansion valve 58 is transferredto the outdoor machine O and expanded again while passing through theoutdoor expansion valve 59, and bypasses the outdoor heat exchanger 60.

The refrigerant bypassed the outdoor heat exchanger 60 is evaporated asreceiving heat from the supply heat exchanger 68 while passing throughthe supply heat exchanger 68, and is circulated to the compressor afterpassing through the 4-way valve 54.

That is, the refrigerant 50 of the heat pump type air conditioner 50 iscondensed at the indoor heat exchanger 56, and is warming the indoor airas evaporated at the supply heat exchanger 68.

The control unit 210 controls the water boil/radiant heat exchangerbypassing valve 184 to be water boil/radiant heat exchanger supply modeas well as operating the heat medium circulation pump 172 for the heatmedium in the heat transfer path 170 to be circulated through the wasteheat recovery heat exchanger 130, hot water supply heat exchanger 70,and the supply heat exchanger 68, and controls the supply heat exchangerbypassing valve 204 to be the supply heat exchanger supply mode.

As the control unit 210 controls the radiant heat exchanger bypassingvalve 194 in accordance with the temperature of the heat medium, itcontrols the radiant heat exchanger bypassing valve 194 to be theradiant heat exchanger supply mode when the temperature of the heatmedium is over the set point, and it controls the radiant heat exchangerbypassing valve 194 to be bypassing mode when the temperature of theheat medium is not more than the set point.

As describing the flowing of the heat medium in the heat transfer path170, the heat medium in the heat transfer path 170 is heated asreceiving heat while passing through the waste heat recovery heatexchanger 130 during the operation of the heat medium circulation pump172, illustrated in FIG. 5, and it streams into the hot water supplyheat exchanger 70 after passing through the water/radiant heat exchangerbypassing valve 184.

The heat medium flown into the water boil heat exchanger 70 heats thehot water supply heat exchanger 70 as transferring heat, and passesthrough or by passes the radiant heat exchanger 160 in accordance withthe temperature condition of the system.

The heat medium passed through or bypassed the radiant heat exchanger160 is supplied to the supply heat exchanger 68 through the supply heatexchanger bypassing valve 204, evaporates the refrigerant as heating therefrigerant passing through the supply heat exchanger 68, and iscirculated to the waste heat recovery heat exchanger 130.

That is, the hot water supply efficiency of the water heat exchanger 70of the co-generation is improved as the heat of the waste heat recoveryheat exchanger 130 is transferred to the hot water supply heat exchanger70 through the heat transfer path 170, and the frosting g and thefollowing problem, reducing of the air warming capacity may be generatedwhen the refrigerant passes through the outdoor heat exchanger 60 areprevented as the supply heat exchanger 68 can stop passing therefrigerant through the outdoor heat exchanger as operating as aevaporator.

The co-generation controls the refrigerant no to pass through theoutdoor heat exchanger 60 as well as operating the heat pump type airconditioner 50 to be the air warming mode, and controls the heat mediumin the heat transfer path 170 not to be circulated through the wasteheat recovery heat exchanger 130, supply heat exchanger 68, and the hotwater supply heat exchanger 70 when the heat pump type air conditioner50 is under the air warming mode without water boiling request,illustrated in FIG. 6.

The heat pump type air conditioner 50 controls the 4-way valve 54 to bethe air warming mode as well as operating the compressor 52 and opensthe outdoor heat exchanger bypassing valve 65 as well as shutting theoutdoor heat exchanger outlet valve 64 and the connection path openingand shutting valve 67.

As describing the flowing of the refrigerant in the heat pump type airconditioner 50, the high-temperature and high-pressure refrigerantcompressed at the compressor 52 is transferred to the indoor machine aspassing through the 4-way valve 54, condensed while passing through theindoor heat exchanger 60 of the indoor machine I, and expanded whilepassing through the indoor expansion valve 58.

The refrigerant expanded at the indoor expansion valve 58 is transferredto the outdoor machine O and expanded again while passing through theoutdoor expansion valve 59, and bypasses the outdoor heat exchanger 60.

The refrigerant bypassed the outdoor heat exchanger 60 is evaporatedwhile passing through the supply heat exchanger 68, and circulated tothe compressor 52 as passing through the 4-way valve 54.

That is, the refrigerant of the heat pump type air conditioner 50 warmsthe indoor air as condensed at the indoor heat exchanger 56 andevaporated at the supply heat exchanger 68.

The control unit 210 operates the heat medium circulation pump 172 forthe heat medium in the heat transfer path 170 to be circulated throughthe waste heat recovery heat exchanger 130 and the supply heat exchanger68, and controls the hot water supply/radiant heat exchanger bypassingvalve 184 to be hot water supply/radiant heat exchanger bypassing modefor the heat medium not to pass through the hot water supply heatexchanger 70.

As describing the flowing of the heat medium of the heat transfer path170, during the operation of heat medium circulation pump 172, asillustrated in FIG. 6, the heat medium in the heat transfer path 170 isheated as receiving heat while passing through the waste heat recoveryheat exchanger 130, then, bypasses the hot water supply heat exchanger70 the radiant heat exchanger 160, and stream into the supply heatexchanger 68.

The heat medium flown into the supply heat exchanger 68 evaporates therefrigerant as heating the refrigerant passing through the supply heatexchanger 68, and is circulated to the waste heat recovery heatexchanger 130.

That is, the heat of the waste heat recovery heat exchanger 130 of theco-generation having the water boil function is not transferred to thehot water supply heat exchanger 70, but is centralized to the supplyheat exchanger 68, and the consumption electricity of the compressor 52is reduced as the pressure is risen with the evaporation of therefrigerant of the heat pump type air-conditioner 50 at the supply heatexchanger 68.

FIG. 7 is a magnified view of the water boil unit of an embodiment ofthe co-generation according to the present invention under the watersupply and heat accumulation water boil mode, FIG. 8 is a magnified viewof the water boil unit of an embodiment of the co-generation accordingto the present invention under the water supply and water boil mode,FIG. 9 is a magnified view of the water boil unit of an embodiment ofthe co-generation according to the present invention under the heataccumulation mode, and FIG. 10 is a magnified view of the water boilunit of an embodiment of the co-generation according to the presentinvention under the circulation mode.

The co-generation, as illustrated in FIGS. 7 to 10, comprises a waterboil recovery inlet temperature sensor 240 composed of a RTD sensor anda temperature sensor gauging the temperature of the water streaming intothe hot water supply heat exchanger 70; a water boil recovery outlettemperature sensor 242 composed of a RTD sensor and a temperature sensorgauging the temperature of the water discharged from the hot watersupply heat exchanger; a water boil inlet temperature sensor 244composed of a RTD sensor and a temperature sensor gauging thetemperature of the heat medium streaming into the hot water supply heatexchanger 70; and a water boil outlet temperature sensor composed of aRTD sensor and a temperature sensor gauging the temperature of the heatmedium discharged from the hot water supply heat exchanger.

The co-generation further comprises a hot water storage tank temperaturesensor 248 composed of a thermistor gauging the temperature of the watersupplied to the water circulation path 82 from the hot water storagetank 80.

Here, the water circulation path flowmeter 234, water boil recoveryinlet temperature sensor 240, water boil recovery outlet temperaturesensor 242, the water boil inlet temperature sensor 244, the water boiloutlet temperature sensor 246, and the hot water storage tanktemperature sensor 248 are installed at the radiant unit EX.

The control unit 210 of the co-generation controls the water supply pump86 a water supply apparatus, the hot water storage tank pump 82 a watersupply apparatus of the hot water storage tank, and the hot water supplyheat exchanger bypassing valve 88 in accordance with the temperatureperceived at the water boil recovery inlet temperature sensor 240, waterboil inlet temperature sensor 244, and the hot water storage tanktemperature sensor 248.

The control unit 210 controls the water boil unit 78 to be the watersupply and heat store water boil mode circulating the water in the hotwater storage tank 80 as supplying the water in the water supply tank 84without connection with the air-cooling/air heating operation asillustrated in FIG. 7 when the temperature of the hot water storage tank80 is the first set point more than the temperature of the water boilrecovery inlet with a water boiling request and the temperature of thewater boil inlet is the second set point more than the temperature ofthe hot water storage tank.

Here, the first set point is as a set temperature deciding the coldwater supplying by the water supply pump 86, it will be described to beset 1 degree C. on the following for the convenience of description, andthe second set point is as a set temperature deciding the heat storingof the hot water storage tank 80, it will be described to be set 3degree C. on the following for the convenience of description.

The control unit 210 controls the hot water supply heat exchangerbypassing valve 88 to be the heat exchanger supply mode as well asoperating the water supply pump and the hot water storage pump 82.

The water in the hot water storage tank 80 is supplied to the watercirculation path 81 by the hot water storage tank pump 82, streams intothe hot water supply heat exchanger 70 after passing through the hotwater supply heat exchanger bypassing valve 88, is heated as taking heatfrom the heat medium while passing through the hot water supply heatexchanger 80, and then, is circulated into the hot water storage tank 80through the water circulation path 81.

The water 84 in the water supply tank is supplied to the water supplypath and supplied to the water circulation path 81 by the water supplypump 86, streams into the hot water supply heat exchanger 70 as mixedwith the hot water supplied to the water circulation path from the hotwater storage tank 80, and is supplied to the hot water storage tank 80through the water circulation path 81 after heated as taking heat fromthe hot water supply heat exchanger 80.

At this time, the hot water supply heat exchanger 70 heats not only thecold water supplied from the water supply tank 84 supplied the heatmedium recovered heat of the waste heat recovery heat exchanger 130, butalso the hot water circulated from the hot water storage tank 80, andthe water boil unit 78 boils water in record time.

The temperature decent scale of the heat medium passing through the hotwater supply heat exchanger 70 is large as heat exchanged with the coldwater and the hot water of the hot water storage tank 80 has a lowertemperature compared with the temperature of the water boil inlet aswell and the heat medium passing through the hot water supply heatexchanger 70 heats as taking much heat of the refrigerant passingthrough the supply heat exchanger 68 while passing through the supplyheat exchanger 68, and it transfers much heat with cold water. whilepassing the hot water supply heat exchanger 70 again.

On the other hand, the control unit 210 controls the water boil unit 78to be the water supply and boil mode circulating the water in the hotwater storage tank 80 to be bypassed the hot water supply heat exchanger70 as supplying the water in the water supply tank 84, as illustrated inFIG. 8 without any consequence of the air-cooling/air heating operationwhen the temperature of the hot water storage tank 80 is the first setpoint more than the temperature of the water boil recovery inlettemperature and has a water boiling request, and the temperature of thewater boil inlet is not the second set point more than the temperatureof the hot water storage tank.

The control unit 210 controls the hot water supply heat exchangerbypassing valve 88 to be the hot water supply heat exchanger bypassingmode as well as operating the water supply pump 86 and the hot waterstorage tank pump 82.

The water in the hot water storage tank 80 is supplied to the watercirculation path 81 by the hot water storage tank pump 82, bypasses thehot water supply heat exchanger 70 as passing through the hot watersupply heat exchanger bypassing valve 88, and is circulated into the hotwater storage tank 80 through the water circulation path 81.

The water in the water supply tank 84 is supplied to the watercirculation path 81 after supplied to the water supply path 83 by thewater supply pump 86, heated with heat taken from the hot water supplyheat exchanger 80 after streaming into the hot water supply heatexchanger 70, and supplied to the hot water storage tank 80 as mixedwith the hot water circulated through the water circulation path 81.

In the hot water supply heat exchanger 70, the heat medium recovered theheat of the waste heat recovery heat exchanger 130 is not heat exchangeddirectly with the hot water has a big temperature variation comparedwith the water boil inlet, but heats only cold water supplied from thewater supply tank 84, and the water supply unit 78 boils water in recordtime.

As the heat medium passed through the hot water supply heat exchanger 70is heat exchanged with the cold water, the decent of temperature of theheat medium is high, heated as taking much heat from the refrigerantpassing through the supply heat exchanger while passing the supply heatexchanger 68, and transfers much heat with cold water while passing thehot water supply heat exchanger 70 again.

When the water boiling is required, the control unit 210 controls thewater-boiling unit to be the heat-storing mode that the cold water inthe water supply tank 84 is not supplied/heated and only the water inthe hot water storing tank 80 is circulated through the hot water supplyheat exchanger 70, as illustrated In FIG. 9, without consequence of theair-cooling/air-warming operation when the temperature of the hot waterstorage tank is not the first set point more than the temperature of thewater boil recovery inlet, and the temperature of the water boil inletis the second set point more than the temperature of the hot waterstorage tank.

The control unit 210 stops operating the water supply pump 86, andcontrols the hot water supply heat exchanger bypassing valve 88 to bethe hot water supply heat exchanger supply mode as well as operating thehot water storage pump 82.

The water in the hot water storage tank 80 is supplied to the watercirculation path 81 by the hot water storage pump 82, streams into thehot water supply heat exchanger 70 after passing through the hot watersupply heat exchanger bypassing valve 88, and is circulated into the hotwater storage tank 80 through the water circulation path 81 after takingthe heat of the heat medium while passing through the hot water supplyheat exchanger 70.

The water boil unit 78 does not supply the water because the temperatureof the hot water storage tank is not the first set point more than thetemperature of the water boil recovery inlet, and only heat the water inthe hot water storage tank 70 rapidly as the temperature of the waterboil inlet is the second set point more than the temperature of the hotwater storage tank.

In the hot water supply heat exchanger 70, the heat medium recoveredheat from the waste heat recovery heat exchanger 130 is heat exchangedwith the hot water in the hot water storage tank 80 having lowertemperature than the heat medium passing through the hot water supplyheat exchanger 70, and the water supply unit boils water rapidly as fastas it can.

The heat medium passed through the hot water supply heat exchanger 70supply heat with the hot water supplied from the hot eater storage tank80, is heated with the heat taken from the refrigerant passing throughthe supply heat exchanger 68 while passing through the supply heatexchanger 68, and then, transfers heat with the hot water while passingthrough the hot water supply heat exchanger 70 again.

When the water boiling is required, and when the temperature of the hotwater storage tank is not the first set point more than the temperatureof the water boil recovery inlet and the temperature of the water boilinlet is not the second set point more than the temperature of the hotwater storage tank, the control unit 210 controls the water boil unit 78to be the circulation mode not supplying/heating the water in the watersupply tank 84 and bypassing the water in the hot water storage tank 80through the hot water supply heat exchanger 70 without consequence ofthe air-cooling/air heating operation as illustrated in FIG. 10.

The control unit 210 stops operating the water supply pump 86 andcontrols the hot water supply heat exchanger bypassing valve 88 to bethe hot water supply heat exchanger bypassing mode as well as operatingthe hot water storage pump 82.

The water in the hot water storage tank 80 is supplied to the watercirculation path 81 by the hot water storage pump 82 and bypasses thehot water supply heat exchanger 70 as passing through the hot watersupply heat exchanger bypassing valve 88, and is circulated into the hotwater storage tank 80 through the water circulation path 81.

That is, the water boil unit 78 doesn't to the water supplying as thetemperature of the hot water storage tank is not the first set pointmore than the temperature of the water boil recovery inlet, and onlycirculates the water in the hot water storage tank 70 as the temperatureof the water boil inlet is not the second set point more than thetemperature of the hot water storage tank.

In the hot water supply heat exchanger 70, the heat medium recovered theheat of the waste heat recovery heat exchanger 130 is not heat exchangedwith the cold water or hot water of the water boil unit 78, but justsupplied to the supply heat exchanger 68.

FIG. 11 is a block diagram of another embodiment of the co-generationaccording to the present invention.

The supply heat exchanger 68′ of the co-generation according to thepresent embodiment is installed in the inside of the outdoor machine O,and the same referential marks are used as other compositions are thesame or similar to the co-generation according to an embodiment of thepresent invention and the detailed description on it is omitted.

A part of the heat transfer path 170 connected with the supply heatexchanger 68′ is arranged as passing through the outdoor machine O.

On the other hand, the present invention isn't limited to theabove-mentioned embodiment, and it is possible to be comprised with thehot water supply heat exchanger 70, the hot water supply heat exchangerbypassing apparatus, the supply heat exchanger 68, and the supply heatexchanger bypassing apparatus 200 without the exhaust gas heat exchanger160 and the exhaust gas heat exchanger bypassing apparatus 190, and itis possible for the engine unit EN and the heat radiant unit EX to becomposed in a single composition, and various embodiments are possiblein the scope the present invention is included.

Reference will now be made in detail as for the effects of theco-generation and the control method of the same of the presentinvention configured as above.

The co-generation and the control method of the same according to thepresent invention has an advantage in that the effective water boil heatis increased as supplying the cold water supplied from the water serviceand the hot water supplied from the hot water storage tank to the hotwater supply heat exchanger properly and heat exchanging with the heatmedium such as an anti freezing solution and etc passing through the hotwater supply heat exchanger.

Moreover, The co-generation and the control method of the same accordingto the present invention has an advantage in that the consumptionelectricity of the compressor is reduced as lowering the condensingpressure by increasing the heat exchanging when the heat mediumcondenses the refrigerant in the supply heat exchanger during theair-cooling operation.

Furthermore, The co-generation and the control method of the sameaccording to the present invention has an advantage in that the amountof water boiling heat is increased as the heat medium taken heat fromthe refrigerant in the supply heat exchanger is supplied to the hotwater supply heat exchanger and used for water boiling again.

1. A co-generation comprising: a hot water supply heat exchanger boilingwater; a heat transfer path connected with the hot water supply heatexchanger for transferring heat; a hot water storage tank connected withthe hot water supply heat exchanger and the water circulation path; ahot water storage pump installed at the water circulation path; a watersupply path connected with the water circulation path; a water supplypump installed at the water supply path; a hot water supply heatexchanger bypassing path formed at the water circulation path; and a hotwater supply heat exchanger bypassing valve controlling the watercirculation path and the hot water supply heat exchanger bypassing path.2. The co-generation according to claim 1, wherein the co-generationfurther comprises a hot water storage tank temperature sensor gaugingthe temperature of the water supplied to the water circulation path fromthe hot water storage tank; a water boil recovery inlet temperaturesensor gauging the temperature of the water streaming into the hot watersupply heat exchanger; a water boil inlet temperature sensor gauging thetemperature of the heat medium streaming into the hot water supply heatexchanger through the heat transfer path; and a control unit controllingthe water supply pump, hot water storage tank pump, and the hot watersupply heat exchanger bypassing valve in accordance with the perceivedtemperature of the hot water storage tank temperature sensor, water boilrecovery inlet temperature sensor, and the water boil inlet temperaturesensor.
 3. The co-generation according to claim 1, wherein theco-generation further comprises a electric generation; a drive sourceoperating the electric generator; and a waste heat recovery heatexchanger recovering the waste heat of the drive source and connectedwith the heat transfer path.
 4. A co-generation comprising: a drivesource operating the electric generator; a waste heat recovery heatexchanger recovering the waste heat of the drive source; a hot watersupply heat exchanger installed for boiling water; an air conditionerair-conditioning indoor air; a supply heat exchanger installed on therefrigerant path of the air conditioner; a heat transfer path connectingthe waste heat recovery heat exchanger, hot water supply heat exchanger,and the supply heat exchanger; a hot water storage tank connected withthe hot water supply heat exchanger and the water circulation path; awater supply path connected with the water circulation path; and a hotwater supply heat exchanger bypassing apparatus bypassing the watersupplied to the water circulation path from the hot water storage tankthrough the hot water supply heat exchanger.
 5. The co-generationaccording to claim 4, wherein the air conditioner is a heat pump typeair conditioner including a compressor, a 4-way valve, an outdoor heatexchanger, an expansion apparatus, and an indoor heat exchanger.
 6. Theco-generation according to claim 5, wherein the heat pump type airconditioner further includes the outdoor heat exchanger bypassingapparatus bypassing the refrigerant through the indoor heat exchanger.7. The co-generation according to claim 5, wherein the supply heatexchanger is installed at the refrigerant path between the 4-way valveand the outdoor heat exchanger.
 8. The co-generation according to claim4, wherein the co-generation further comprises a hot water supply heatexchanger bypassing apparatus bypassing the heat of the waste heatrecovery heat exchanger through the hot water supply heat exchanger; anda supply heat exchanger bypassing apparatus bypassing the heat of thewaste heat recovery heat exchanger through the supply heat exchanger. 9.The co-generation according to claim 4, wherein the co-generationfurther comprises a radiant heat exchanger radiating heat to outside asinstalled between the hot water supply heat exchanger and the supplyheat exchanger in the heat transfer path; water boil/radiant heatexchanger bypassing apparatus bypassing the heat of the waste heatrecovery heat exchanger through the hot water supply heat exchanger andradiant heat exchanger; a radiant heat exchanger bypassing apparatusbypassing the heat of the waste heat recovery heat exchanger through theradiant heat exchanger; and a supply heat exchanger bypassing apparatusbypassing the heat of the waste heat recovery heat exchanger through thesupply heat exchanger.
 10. The co-generation according to claim 4,wherein a check valve is installed at the water supply path.
 11. Theco-generation according to claim 4, wherein the water supply path isconnected with the water supply tank.
 12. The co-generation according toclaim 4, wherein the co-generation further comprises a hot water storagetank water supply apparatus supplying the water in the hot water storagetank to the water circulation path; and a water supply apparatussupplying water to the water supply path.
 13. The co-generationaccording to claim 12, wherein the hot water supply heat exchangerbypassing apparatus includes a hot water supply heat exchanger bypassingpath; and a hot water supply heat exchanger bypassing valve controllingthe water circulation path and the hot water supply heat exchangerbypassing path.
 14. The co-generation according to claim 13, wherein acheck valve is installed between the hot water storage tank and the hotwater supply heat exchanger bypassing valve in the water circulationpath.
 15. The co-generation according to claim 13, wherein theco-generation further comprises a hot water storage temperature sensorgauging the temperature of the water supplied to the water circulationpath from the hot water storage tank; a water boil recover inlettemperature sensor; a water boil inlet temperature sensor gauging thetemperature of the heat medium streaming into the hot water supply heatexchanger; and a control unit controlling the water supply apparatus,the hot water storage tank water supply apparatus and the hot watersupply heat exchanger bypassing valve in accordance with the perceivedtemperature of the hot water storage tank temperature sensor, water boilrecover inlet temperature sensor, and the water boil inlet temperaturesensor.
 16. The co-generation according to claim 15, wherein the hotwater storage tank water supply apparatus is a hot water storage tankpump installed at the water circulation path, and the water supplyapparatus is a water supply pump installed at the water supply path. 17.The control method of the co-generation according to claim 16, whereinthe cogeneration operates the water supply pump and the hot waterstorage pump, and controls the hot water supply heat exchanger bypassingvalve to be the hot water supply heat exchanger supply mode when thetemperature of the hot water storage tank is the first set point morethan the temperature of the water boil recover inlet and the temperatureof the water boil inlet is the second set point more than thetemperature of the hot water storage tank.
 18. The control method of theco-generation according to claim 16, wherein the co-generator operatesthe water supply pump and the hot water storage tank pump, and controlsthe hot water supply heat exchanger bypassing valve to be the hot watersupply heat exchanger bypassing mode when the temperature of the hotwater storage tank is the first set point more than the temperature ofthe water boil recover inlet and the temperature of the water boil inletis not the second set point more than the temperature of the hot waterstorage tank.
 19. The control method of the co-generation according toclaim 16, wherein the co-generation operates the hot water storage tankpump as well as stopping the operation of the water supply pump, andcontrols the hot water supply heat exchanger bypassing valve to be thehot water supply heat exchanger supply mode when the temperature of thehot water storage tank is not the first set point more than thetemperature of the temperature of the water boil recover inlet and thetemperature of the water boil inlet is the second set point more thanthe temperature of the hot water storage tank.
 20. The control method ofthe co-generation according to claim 16, wherein the co-generationoperates the hot water storage tank pump as well as stopping theoperation of the water supply pump, and controls the hot water supplyheat exchanger bypassing valve to be the hot water supply heat exchangerbypassing mode when the temperature of the hot water storage tank is notthe first set point more than the temperature of the water boil recoverinlet and the temperature of the water boil inlet is not the second setpoint more than the temperature of the hot water storage tank.